JP7126617B2 - Heat exchange element and heat exchange ventilator - Google Patents

Description

The present invention relates to heat exchange elements and heat exchange ventilators for exchanging heat between air streams.

2. Description of the Related Art Conventionally, a heat exchange ventilator is known that exchanges heat between an air supply flow from the outdoors to the room and an exhaust air flow from the room to the outdoors. Ventilation using a heat exchange ventilator can improve the efficiency of indoor cooling and heating and the efficiency of dehumidification and humidification, and reduce the energy used for indoor air conditioning.

A heat exchange ventilator comprises a heat exchange element for exchanging heat. The heat exchange element is provided with a supply air path and an exhaust air path. The supply air path and the exhaust air path are air paths independent of each other with a partition member interposed therebetween. In the heat exchange element, heat is transferred between the supply air flow through the supply air passage and the exhaust air flow through the exhaust air passage through the partition member. A heat exchange element is required to have improved heat exchange efficiency.

Patent Literature 1 discloses a technique for improving the heat exchange efficiency by increasing the heat transfer area and generating turbulence in the airflow by providing unevenness on the partition member.

JP-A-4-273993

However, in the technique disclosed in Patent Document 1, the airflow is separated from the heat transfer surface of the partition member due to excessive development of turbulence at the convex portions of the partition member or excessive depth of the concave portions of the partition member. Because it is easy to heat, a region with poor heat transfer efficiency may be created. As a result, there is a problem that improvement in heat exchange efficiency may be insufficient.

The present invention has been made in view of the above, and an object of the present invention is to obtain a heat exchange element capable of improving heat exchange efficiency.

In order to solve the above-described problems and achieve the object, a heat exchange element according to the present invention includes a first heat transfer unit forming a first air passage and a second heat transfer unit forming a second air passage. Prepare. The first air passage and the second air passage include a first width air passage extending from the air flow inlet toward the downstream side along the flow direction of the air flow, and a first width air passage downstream of the first width air passage. and two or more second width air passages formed by branching the air passage into two or more. The air passage width of the second width air passage is narrower than the air passage width of the first width air passage. The length of the first width air passage along the flow direction of the airflow is equal to or less than the length of the approach section of the first width air passage. The length of the second width air passage along the flow direction of the air flow is equal to or less than the length of the approach section of the second width air passage. The length LL of the approach section is expressed by the formula LL=0.056×Re×de, where Re is the Reynolds number and de is the equivalent diameter of the first air passage or the second air passage.

ADVANTAGE OF THE INVENTION According to this invention, it is effective in the ability to improve heat exchange efficiency.

1 is an exploded perspective view showing a heat exchange element according to Embodiment 1 of the present invention; 1 is a perspective view of a heat transfer unit of a heat exchange element according to Embodiment 1 of the present invention; FIG. A perspective view of a heat transfer unit of a heat exchange element according to Embodiment 2 of the present invention. A perspective view of a heat transfer unit of a heat exchange element according to Embodiment 3 of the present invention. A perspective view of a heat transfer unit of a heat exchange element according to Embodiment 4 of the present invention. Schematic diagram showing a heat exchange ventilator according to Embodiment 5 of the present invention

BEST MODE FOR CARRYING OUT THE INVENTION A heat exchange element and a heat exchange ventilator according to embodiments of the present invention will be described in detail below with reference to the drawings. In addition, this invention is not limited by this embodiment.

Embodiment 1.
FIG. 1 is an exploded perspective view showing a heat exchange element 1 according to Embodiment 1 of the present invention. The heat exchange element 1 includes a plurality of first heat transfer units 2 a forming first air passages 5 and a plurality of second heat transfer units 2 b forming second air passages 6 . The first heat transfer units 2a and the second heat transfer units 2b are alternately stacked. Hereinafter, the first heat transfer unit 2a and the second heat transfer unit 2b may be collectively referred to as "heat transfer unit 2".

Each heat transfer unit 2 includes one partition member 3 and a plurality of spacing members installed on the partition member 3 to form a first air passage 5 or a second air passage 6 between the adjacent partition members 3. 4. That is, the heat exchange element 1 includes a plurality of partition members 3 spaced apart from each other, and a plurality of spacing members 4 that maintain the spacing between the partition members 3 .

A partition member 3 partitions between the first air passage 5 and the second air passage 6 . The first air passages 5 and the second air passages 6 are provided alternately with the partition member 3 interposed therebetween. The first air flow 7 is a supply air flow from the outdoor to the indoor. The second air flow 8 is the exhaust flow from the room to the outside. A first air flow 7 flows through the first air passage 5 . A second air flow 8 flows through the second air passage 6 . The heat exchange element 1 is a cross-flow type total heat exchange element in which the flow direction of the first air flow 7 and the flow direction of the second air flow 8 are orthogonal to each other. In the heat exchange element 1 , heat is transferred between the first airflow 7 and the second airflow 8 via the partition member 3 . Hereinafter, the flow direction of the air flow may be referred to as "air flow direction", and the direction orthogonal to the flow direction of the air flow may be referred to as "perpendicular direction".

The partition member 3 is a plate-like member formed in a rectangular shape in a plan view. For the partition member 3, a functional paper made from highly beaten pulp, a composite resin film using a hydrophilic resin, or the like is used. The partition member 3 may be one to which a hygroscopic agent is added to promote hygroscopic action. As the hygroscopic agent, materials having deliquescent properties such as lithium chloride and calcium chloride, materials having moderate moisture absorption and desorption properties such as desiccant agents, and materials having adsorption properties such as zeolite and silica gel may be used.

The partition member 3 may be made of a resin plate, a resin film, or the like, which does not have moisture permeability. In this case, it works as a sensible heat exchange element that exchanges only temperature, and PET (Polyethylene Terephthalate), PP (Polypropylene), ABS (Acrylonitrile Butadiene Styrene), PS (Polystyrene), etc. are used for the resin plate. A composite resin film using a thin film of polyurethane, polyethylene, or the like may be used as the resin film. If a thin film is used, it is preferred to use a non-woven fabric such as polyester for manufacturing strength and stiffness.

Although the shape of the spacing member 4 is not particularly limited, it is a quadrangular prism in this embodiment. The spacing member 4 extends along the direction of air flow. The spacing member 4 requires a material and structure that accurately maintains the spacing dimension of the partition member 3 . The spacing member 4 is made of square timber using a resin material such as PP, ABS, or PS, square timber made of paper using pulp mold, PET or PP resin material molded into a hollow, hollow made by bending paper or a resin film. You may form with a member. If the partition member 3 does not have a moisture permeation function, the interval holding member 4 and the partition member 3 can be integrally molded from the same material. By doing so, productivity can be increased and costs can be reduced. In addition, the weight of the heat exchange element 1 can be reduced by forming the spacing member 4 into a hollow shape.

FIG. 2 is a perspective view of the heat transfer unit 2 of the heat exchange element 1 according to Embodiment 1 of the present invention. A plurality of spacing members 4 having different lengths are installed on one partition member 3 . In this embodiment, three types of spacing members 4 having different lengths along the direction of air flow are used. Hereinafter, the longest spacing member 4 is the "first spacing member 41", the second longest spacing member 4 is the "second spacing member 42", and the shortest spacing member 4 is the "third spacing member 43". ”. In this embodiment, two first spacing members 41, two second spacing members 42, and three third spacing members 43 are installed. In the following description, upstream and downstream mean upstream and downstream along the flow direction of the airflow.

The first spacing member 41 is a member that defines the air passage width X<b>1 of the first width air passage 9 . The first spacing member 41 is installed over the entire length of both ends of the partition member 3 along the direction perpendicular to the flow direction of the airflow. A first width air passage 9 is formed between the two first spacing members 41 on the upstream side of the second spacing member 42 . The first width air passage 9 will be described later in detail.

The second spacing member 42 is a member that defines the air passage width X2 of the second width air passage 10 . The second spacing member 42 is installed between the two first spacing members 41 . The two second spacing members 42 are spaced apart from each other along the orthogonal direction. The interval between the two second spacing members 42 and the interval between the adjacent second spacing member 42 and the first spacing member 41 are equal. The second spacing member 42 extends upstream from the leeward end 31 of the partition member 3 . The windward side end surface 42 a of the second spacing member 42 is located downstream of the windward side end surface 41 a of the first spacing member 41 . A second width air passage 10 is formed upstream of the third spacing member 43 between the two second spacing members 42 . A second width air passage 10 is formed upstream of the third spacing member 43 between the adjacent second spacing member 42 and first spacing member 41 . The second width air passage 10 will be described later in detail.

The third spacing member 43 is a member that defines the air passage width X3 of the third width air passage 11 . The three third spacing members 43 are spaced apart from each other along the orthogonal direction. One third spacing member 43 is installed between the adjacent first spacing member 41 and the second spacing member 42 and between the adjacent second spacing members 42 . The third spacing member 43 extends upstream from the leeward end 31 of the partition member 3 . The windward side end face 43 a of the third spacing member 43 is located downstream of the windward side end face 41 a of the first spacing member 41 and the windward side end face 42 a of the second spacing member 42 . The spacing between the adjacent third spacing member 43 and the first spacing member 41 and the spacing between the adjacent second spacing member 42 and the first spacing member 41 are equal. A third width air passage 11 is formed between the adjacent third spacing member 43 and the first spacing member 41 . A third width air passage 11 is formed between the adjacent third spacing member 43 and second spacing member 42 . The third width air passage 11 will be described later in detail.

Next, referring to FIG. 2, the first width air duct 9, the second width air duct 10 and the third width air duct 11 will be described. Note that the first air passage 5 and the second air passage 6 differ only in the direction in which the airflow flows, and the other configurations are the same. 6 is omitted. The air passage width of the first air passage 5 gradually narrows toward the downstream side along the air flow direction. The first air passage 5 includes a first width air passage 9 extending from an inlet 22 of the first air flow 7 toward the downstream side along the air flow direction, and a first width air passage 9 downstream of the first width air passage 9. two or more second width air passages 10 formed by branching the air passage 9 into two or more; and two or more third width air passages 11 formed. In this embodiment, the case where one first width air passage 9, three second width air passages 10, and six third width air passages 11 are provided is illustrated. It is not intended to limit the number.

The air passage width X1 of the first width air passage 9 is the widest among the first air passages 5 . The first width air duct 9 extends with a first air duct length Y1 along the direction of air flow.

The air passage width X2 of the second width air passage 10 is narrower than the air passage width X1 of the first width air passage 9 . The second width air passage 10 extends with a second air passage length Y2 along the direction of air flow.

The air passage width X3 of the third width air passage 11 is narrower than the air passage width X1 of the first width air passage 9 and the air passage width X2 of the second width air passage 10 . The third width air duct 11 extends with a third air duct length Y3 along the direction of air flow. The air passage height Z1 of the first air passage 5 is constant over the entire length in the air flow direction. That is, the heights of the first width air duct 9, the second width air duct 10 and the third width air duct 11 are the same.

The first air passage length Y1 of the first width air passage 9, the second air passage length Y2 of the second width air passage 10, and the third air passage length Y3 of the third width air passage 11 are the lengths of the run-up section. less than or equal to The run-up section refers to a section in which turbulence in the airflow occurs moderately. The length LL1 of the approach section of the first width air passage 9 is represented by the following formula (1). Let Re be the Reynolds number of the first air flow 7 . Let D1 be the equivalent diameter of the first width air passage 9 . The equivalent diameter of the first width air duct 9 is the inner diameter of a cylindrical air duct that can be regarded as equivalent to the first width air duct 9 from the viewpoint of air flow.
LL1=0.056×Re×D1 (1)

The first air passage length Y1 of the first width air passage 9 along the flow direction of the air flow is preferably equal to or less than the length LL1 of the approach section of the first width air passage 9 . Therefore, it is preferable that the following formula (2) holds.
Y1≦0.056×Re×D1 (2)

The length LL2 of the approach section of the second width air passage 10 is represented by the following formula (3). Re is the same as in formula (1) above. D2 is the equivalent diameter of the second width air passage 10 . The equivalent diameter of the second width air duct 10 is the inner diameter of a cylindrical air duct that can be regarded as equivalent to the second width air duct 10 from the viewpoint of air flow.
LL2=0.056×Re×D2 (3)

The second air passage length Y2 of the second width air passage 10 along the flow direction of the airflow is preferably equal to or less than the length LL2 of the approach section of the second width air passage 10 . Therefore, it is preferable that the following formula (4) holds.
Y2≦0.056×Re×D2 (4)

The length LL3 of the approach section of the third width air passage 11 is represented by the following formula (5). Re is the same as in formula (1) above. Let D3 be the equivalent diameter of the third width air passage 11 . The equivalent diameter of the third width air duct 11 is the inner diameter of a cylindrical air duct that can be regarded as equivalent to the third width air duct 11 from the viewpoint of air flow.
LL3=0.056×Re×D3 (5)

A third air passage length Y3 of the third width air passage 11 along the flow direction of the air flow is preferably equal to or less than the length LL3 of the approach section of the third width air passage 11 . Therefore, it is preferable that the following formula (6) holds.
Y3≦0.056×Re×D3 (6)

An equivalent diameter D1 of the first width air passage 9 is represented by the following formula (7). Let S1 be the air passage cross-sectional area of the first width air passage 9 . L1 is the peripheral length of the cross section of the first width air passage 9, that is, the length of the wet edge of the first width air passage 9. As shown in FIG. The unit of air passage cross-sectional area is m ² .
D1=4×S1/L1 (7)

The equivalent diameter D2 of the second width air passage 10 is represented by the following formula (8). Let S2 be the air passage cross-sectional area of the second width air passage 10 . L2 is the peripheral length of the cross section of the second width air passage 10, that is, the length of the wet edge of the second width air passage 10. The unit of air passage cross-sectional area is m ² .
D2=4×S2/L2 (8)

The equivalent diameter D3 of the third width air passage 11 is represented by the following formula (9). Let S3 be the air passage cross-sectional area of the third width air passage 11 . L3 is the perimeter of the cross section of the third width air duct 11, that is, the length of the wet edge of the third width air duct 11. The unit of air passage cross-sectional area is m ² .
D3=4×S3/L3 (9)

In this embodiment, the first width air duct 9 is assumed to have a rectangular cross section, and the air duct cross-sectional area S1 of the first width air duct 9 is represented by the following formula (10). Z1 is the air passage height of the first air passage 5;
S1=X1×Z1 (10)

In this embodiment, the second width air duct 10 is assumed to have a rectangular cross section, and the air duct cross-sectional area S2 of the second width air duct 10 is expressed by the following formula (11).
S2=X2×Z1 (11)

In this embodiment, the third width air duct 11 is considered to have a rectangular cross section, and the air duct cross-sectional area S3 of the third width air duct 11 is represented by the following formula (12).
S3=X3×Z1 (12)

The wetting edge length L1 of the first width air passage 9 is represented by the following formula (13).
L1=2×(X1+Z1) (13)

The wetting edge length L2 of the second width air passage 10 is represented by the following formula (14).
L2=2×(X2+Z1) (14)

The wetting edge length L3 of the third width air passage 11 is represented by the following formula (15).
L3=2×(X3+Z1) (15)

The Reynolds number Re of the first width air passage 9 is represented by the following formula (16). Let V1 be the average flow velocity of the first airflow 7 in the first width air passage 9 . The unit of V shall be meters per second. Let ν be the dynamic viscosity coefficient of the first air flow 7 in the first air passage 5 . The unit of ν is square meters per second. When the temperature of air under atmospheric pressure is 20° C., the kinematic viscosity coefficient ν is generally used to be 1.5×10 ⁻⁶ m ² /s.
Re=(D1)×(V1)/(ν) (16)

The average flow velocity V1 of the first airflow 7 in the first width air passage 9 is represented by the following formula (17). Let Q1 be the flow rate of the first airflow 7 flowing through the first width air passage 9 . The unit of Q shall be cubic meters.
V1=Q1/S1 (17)

The Reynolds number Re of the second width air passage 10 is represented by the following formula (18). Let V2 be the average flow velocity of the first airflow 7 in the second width air passage 10 .
Re=(D2)×(V2)/(ν) (18)

The average flow velocity V2 of the first airflow 7 in the second width air passage 10 is represented by the following formula (19). Let Q2 be the flow rate of the first airflow 7 flowing through the second width air passage 10 .
V2=Q2/S2 (19)

The Reynolds number Re of the third width air passage 11 is represented by the following formula (20). Let V3 be the average flow velocity of the first airflow 7 in the third width air passage 11 .
Re=(D3)×(V3)/(ν) (20)

The average flow velocity V3 of the first airflow 7 in the third width air passage 11 is represented by the following formula (21). Let Q3 be the flow rate of the first airflow 7 flowing through the third width air passage 11 .
V3=Q3/S3 (21)

In the present embodiment, the length LL1 of the run-up section of the first width air passage 9 obtained by the above formula and the first air passage length Y1 of the first width air passage 9 are made equal. Also, the length LL2 of the run-up section of the second width air passage 10 and the second air passage length Y2 of the second width air passage 10 are made equal. Also, the length LL3 of the run-up section of the third width air passage 11 and the length Y3 of the third width air passage 11 are made equal.

Next, the effects of the heat exchange element 1 will be described.

In the present embodiment, the first air passage 5 and the second air passage 6 include one first width air passage 9 extending from the inlet 22 toward the downstream side along the flow direction of the air flow, Three second width air passages 10 formed by branching the first width air passage 9 into three on the downstream side of the air passage 9, and the second width air passage 10 on the downstream side of the second width air passage 10. and six third width air passages 11 formed by branching into six. In addition, the air passage width X2 of the second width air passage 10 is narrower than the air passage width X1 of the first width air passage 9, and the air passage width X3 of the third width air passage 11 is smaller than that of the second width air passage 10. It is narrower than the air passage width X2. Therefore, the run-up section is repeatedly generated over the entire length of the first air passage 5 and the second air passage 6 in the air flow direction, and the separation of the air flow from the heat transfer surface of the partition member 3 is suppressed while the air flow is generated. Turbulence can be moderately generated. By suppressing the separation of the air flow from the heat transfer surface of the partition member 3, the contact area of the air contacting the heat transfer surface can be increased, and by generating turbulence in the air flow, the first air passage 5 and the second air passage 5 are separated. The heat transfer rate and mass transfer rate to the inner wall surface of the second air passage 6 are increased. Thereby, the total heat exchange efficiency of the heat exchange element 1 can be improved. According to experiments and studies by the present inventor, the length of each width air passage 9, 10, 11 is made longer than the run-up section, and the air flow in the run-up space and the air flow after passing the run-up section , it was found that the turbulence of the air flow is more likely to occur in the run-up section than after the run-up section. In the air passage of the heat exchange element 1, in which air flows while conducting heat and substance transfer to the inner wall surface of the air passage, the temperature and humidity of the air flow are mixed due to turbulence of the air flow, resulting in a temperature boundary layer and a humidity boundary layer. Boundary layer is destroyed. Therefore, the heat transfer coefficient and the mass transfer coefficient with respect to the inner wall surfaces of the first air passage 5 and the second air passage 6 are higher in the run-up section than after the run-up section.

In the conventional technology in which unevenness is provided on the partition member, the airflow tends to be separated from the heat transfer surface of the partition member, so that a region with poor heat transfer efficiency may be created. As a result, the total heat exchange efficiency of the heat exchange element may not improve. On the other hand, in the present embodiment, by repeatedly generating the run-up section over the entire length of the first air passage 5 and the second air passage 6 in the air flow direction, the air from the heat transfer surface of the partition member 3 Flow separation can be suppressed. As a result, regions with poor heat transfer efficiency can be reduced as compared with the conventional technology, so that the total heat exchange efficiency of the heat exchange element 1 can be improved.

In the present embodiment, when the partition member 3 and the spacing member 4 are manufactured separately, they are bonded by bonding with an adhesive, or by heat welding if the material is resin, thereby forming the structure shown in FIG. The heat transfer unit 2 can be made strong. As a result, the structural strength of the heat exchange element 1 can be improved even when a plurality of heat transfer units 2 are stacked with the length direction of the spacing members 4 perpendicular to each other as shown in FIG.

Embodiment 2.
FIG. 3 is a perspective view of the heat transfer unit 2 of the heat exchange element 1 according to Embodiment 2 of the present invention. In addition, in Embodiment 2, the same code|symbol is attached|subjected about the part which overlaps with above-mentioned Embodiment 1, and description is abbreviate|omitted.

The shape of the spacing member 4 is a corrugated shape in this embodiment. The spacing member 4 is formed in a generally triangular shape that is convex in the direction away from the partition member 3 . The cross-sectional shapes of the first width air duct 9, the second width air duct 10 and the third width air duct 11 are trapezoidal or triangular. The inside of the spacing member 4, that is, the space surrounded by the spacing member 4 and the partition member 3 also serves as an air passage.

In this embodiment, four types of spacing members 4 having different lengths along the direction of air flow are used. Hereinafter, the longest spacing member 4 is referred to as "first spacing member 41", and the second longest spacing member 4 is referred to as "second spacing member 42". Further, the third longest spacing member 4 is called a "third spacing member 43", and the shortest spacing member 4 is called a "fourth spacing member 44". In this embodiment, two first spacing members 41, one second spacing member 42, two third spacing members 43, and four fourth spacing members 44 are installed. Illustrate.

The first spacing member 41 is a member that defines the air passage width X<b>1 of the first width air passage 9 . The first spacing member 41 is installed over the entire length of both ends of the partition member 3 along the direction perpendicular to the flow direction of the airflow. A first width air passage 9 is formed between the two first spacing members 41 on the upstream side of the second spacing member 42 . The first width air passage 9 will be described later in detail.

The second spacing member 42 is a member that defines the air passage width X2 of the second width air passage 10 . The second spacing member 42 is installed between the two first spacing members 41 . The spacing between the adjacent second spacing members 42 and one first spacing member 41 and the spacing between the adjacent second spacing members 42 and the other first spacing member 41 are equal. That is, the second spacing member 42 is installed at an intermediate position between the two first spacing members 41 in the orthogonal direction. The second spacing member 42 extends upstream from the leeward end 31 of the partition member 3 . The windward end of the second spacing member 42 is located downstream of the windward end of the first spacing member 41 . A second width air passage 10 is formed upstream of the third spacing member 43 between the adjacent second spacing member 42 and first spacing member 41 . The second width air passage 10 will be described later in detail.

The third spacing member 43 is a member that defines the air passage width X3 of the third width air passage 11 . The two third spacing members 43 are spaced apart from each other along the orthogonal direction. One third spacing member 43 is installed between each adjacent first spacing member 41 and second spacing member 42 . The third spacing member 43 extends upstream from the leeward end 31 of the partition member 3 . The windward end of the third spacing member 43 is located downstream of the windward end of the first spacing member 41 and the windward end of the second spacing member 42 . The interval between the adjacent third spacing member 43 and the first spacing member 41 and the interval between the adjacent third spacing member 43 and the second spacing member 42 are equal. A third width air passage 11 is formed upstream of the fourth spacing member 44 between the adjacent third spacing member 43 and first spacing member 41 . A third width air passage 11 is formed upstream of the fourth spacing member 44 between the adjacent third spacing member 43 and second spacing member 42 . The third width air passage 11 will be described later in detail.

The fourth spacing member 44 is a member that defines the air passage width X4 of the fourth width air passage 12 . The four fourth spacing members 44 are spaced apart from each other along the orthogonal direction. One fourth spacing member 44 is provided between the adjacent first spacing member 41 and the third spacing member 43 and between the adjacent second spacing member 42 and the third spacing member 43. are installed one by one. The fourth spacing member 44 extends upstream from the leeward end 31 of the partition member 3 . The windward end of the fourth spacing member 44 is positioned further than the windward end of the first spacing member 41 , the windward end of the second spacing member 42 , and the windward end of the third spacing member 43 . located downstream. The distance between the adjacent fourth distance maintaining member 44 and the first distance maintaining member 41, the distance between the adjacent fourth distance maintaining member 44 and the second distance maintaining member 42, and the distance between the adjacent fourth distance maintaining member 44 and the second distance maintaining member 42 3 The spacing with the spacing member 43 is equal. A fourth width air passage 12 is formed between the adjacent fourth spacing member 44 and the first spacing member 41 . A fourth width air passage 12 is formed between the adjacent fourth spacing member 44 and the second spacing member 42 . A fourth width air passage 12 is formed between the adjacent fourth spacing member 44 and third spacing member 43 . The fourth width air passage 12 will be described later in detail.

Next, the first width air passage 9, the second width air passage 10, the third width air passage 11 and the fourth width air passage 12 will be described. Note that the first air passage 5 and the second air passage 6 differ only in the flow direction of the air flow, and the other configurations are the same. 6 is omitted. The air passage width of the first air passage 5 gradually narrows toward the downstream side along the air flow direction. The first air passage 5 includes a first width air passage 9 extending from the inlet 22 toward the downstream side along the air flow direction, and two first width air passages 9 on the downstream side of the first width air passage 9. and two or more second width air passages 10 formed by branching as described above. Further, the first air passage 5 includes two or more third width air passages 11 formed by branching the second width air passage 10 into two or more on the downstream side of the second width air passage 10, and a third and two or more fourth width air passages 12 formed by branching the third width air passage 11 into two or more on the downstream side of the width air passage 11 . In this embodiment, one first width air passage 9, two second width air passages 10, four third width air passages 11, and eight fourth width air passages 12 are provided. However, it is not intended to limit the number of each width air passage 9, 10, 11, 12.

The air passage width X1 of the first width air passage 9 is the widest among the first air passages 5 . The first width air duct 9 extends with a first air duct length Y1 along the direction of air flow.

The air passage width X2 of the second width air passage 10 is narrower than the air passage width X1 of the first width air passage 9 . The second width air passage 10 extends with a second air passage length Y2 along the direction of air flow.

The air passage width X3 of the third width air passage 11 is narrower than the air passage width X1 of the first width air passage 9 and the air passage width X2 of the second width air passage 10 . The third width air duct 11 extends with a third air duct length Y3 along the direction of air flow.

The air passage width X4 of the fourth width air passage 12 is the narrowest among the first air passages 5 . The fourth width air duct 12 extends along the air flow direction with a fourth air duct length Y4. The air passage height Z2 of the first air passage 5 is constant over the entire length in the air flow direction. That is, the heights of the first width air duct 9, the second width air duct 10, the third width air duct 11 and the fourth width air duct 12 are the same.

The cross-sectional shapes of the first air duct 5 and the second air duct 6 according to the present embodiment are different from the cross-sectional shapes of the first air duct 5 and the second air duct 6 according to the first embodiment. Therefore, it is necessary to consider the equivalent diameter and the length of the run-up section that changes accordingly. That is, for the first air passage 5 and the second air passage 6 according to the second embodiment as well, the length of the approach section can be obtained by calculating the equivalent diameter and the Reynolds number. The cross-sectional shapes of the first air duct 5 and the second air duct 6 may be regarded as trapezoidal or approximately triangular. Since the cross-sectional shape of the first air duct 5 of the present embodiment is a general geometric shape, the description of the cross-sectional area of the air duct and the length of the wetted edge will be omitted.

When using the corrugated space holding member 4, the first space holding member 41, the second space holding member 42, the third space holding member 43 and the fourth space holding member 44 having different lengths are molded or folded. , and each of the manufactured spacing members 4 can be joined to the partition member 3 . In addition, one long corrugated member was prepared, cut to the length of the first spacing member 41, the second spacing member 42, the third spacing member 43, and the fourth spacing member 44, and cut. Each of the spacing members 4 can also be joined to the partition member 3 .

3, the air passage width X1, the air passage width X2, the air passage width X3, the air passage width X4, the first air passage length Y1, the second air passage length Y2, the third air passage length Y3, The first spacing member 41, the second spacing member 42, the third spacing member 43, and the fourth spacing member 41, the second spacing member 42, the third spacing member 43, and the fourth spacing member 41, the second spacing member 42, and the third spacing member 43 are formed at once by vacuum forming or press molding so that the dimensional relationship of the fourth air path length Y4 and the air path height Z2 is achieved. A fourth spacing member 44 can also be manufactured. Further, a corrugated member having a length longer than the first spacing member 41 is prepared by extrusion molding, and the corrugated member is cut to form the first spacing member 41, the second spacing member 42, and the third spacing member. 43 and fourth spacing member 44 can also be manufactured.

In the case of using the paper corrugating technique, paper with holes periodically opened is passed through a core manufacturing machine to form the first spacing member 41, the second spacing member 42, the third spacing member 43 and the fourth spacing member 43. The spacing member 44 can also be manufactured. In the case of using a conventional cardboard manufacturing technique, the first spacing member 41, the second spacing member 42, the third spacing member 43, and the fourth spacing member 44 are formed by cutting the corrugated cardboard. can also be manufactured.

When the corrugated spacing member 4 is used, the pressure loss of the heat exchange element 1 can be reduced because the interior of the spacing member 4 also becomes a hollow air passage. Moreover, continuous production can be performed by taking advantage of the productivity of corrugated manufacturing. Thereby, the heat exchange element 1 with reduced pressure loss and high productivity can be obtained.

Embodiment 3.
FIG. 4 is a perspective view of the heat transfer unit 2 of the heat exchange element 1 according to Embodiment 3 of the present invention. In addition, in Embodiment 3, the same code|symbol is attached|subjected about the part which overlaps with above-mentioned Embodiment 1, and description is abbreviate|omitted.

This embodiment differs from the first embodiment in that the second spacing member 42 is offset from the third spacing member 43 on the upstream side along the air flow direction. In this embodiment, two first spacing members 41, three second spacing members 42, and six third spacing members 43 are installed. Although the third spacing member 43 is longer than the second spacing member 42 in this embodiment, the lengths of both may be made equal, or the second spacing member 42 may be longer than the third spacing member 43. may

The third spacing member 43 is installed between the two first spacing members 41 . The six third spacing members 43 are spaced apart from each other along the orthogonal direction. The third spacing member 43 extends upstream from the leeward end 31 of the partition member 3 . The windward side end face 43 a of the third spacing member 43 is located downstream of the windward side end face 41 a of the first spacing member 41 and the windward side end face 42 a of the second spacing member 42 . The intervals between adjacent third spacing members 43 are equal. The interval between adjacent third spacing members 43 is wider than the interval between adjacent third spacing member 43 and first spacing member 41 .

A third width air passage 11 is formed between adjacent third spacing members 43 . Hereinafter, the third width air passages 11 formed between the adjacent third spacing members 43 are referred to as "third main width air passages 11a". A third width air passage 11 is formed between the adjacent third spacing member 43 and the first spacing member 41 . Hereinafter, the third width air duct 11 formed between the adjacent third spacing member 43 and the first spacing member 41 is referred to as "third sub-width air duct 11b". The air passage width X32 of the third sub-width air passage 11b is half the air passage width X31 of the third main width air passage 11a in this embodiment. The air passage width X31 of the third main width air passage 11a and the air passage width X32 of the third sub-width air passage 11b are narrower than the air passage width X1 of the first width air passage 9 . In the present embodiment, the case of providing five third main width air passages 11a and two third sub width air passages 11b is exemplified. It is not intended to limit the number of

The second spacing member 42 is installed between the two first spacing members 41 . The three second spacing members 42 are spaced apart from each other along the orthogonal direction. The second spacing member 42 is offset from the third spacing member 43 on the upstream side along the air flow direction. The second spacing member 42 is arranged upstream of the third main width air passage 11a. The second spacing member 42 is installed every other one with respect to the five third main width air passages 11a. The intervals between adjacent second spacing members 42 are equal. The interval between adjacent second spacing members 42 is wider than the interval between adjacent second spacing members 42 and first spacing members 41 .

A second width air passage 10 is formed between the adjacent second spacing members 42 . Hereinafter, the second width air passages 10 formed between the adjacent second spacing members 42 are referred to as "second main width air passages 10a". A second width air passage 10 is formed between the second spacing member 42 and the first spacing member 41 adjacent to each other. Hereinafter, the second width air duct 10 formed between the adjacent second spacing member 42 and the first spacing member 41 is referred to as "second sub-width air duct 10b". The air passage width X22 of the second sub-width air passage 10b is formed to be half the air passage width X21 of the second main width air passage 10a in the present embodiment. In this embodiment, the case of providing two second main width air passages 10a and two second sub width air passages 10b is exemplified. It is not intended to limit the number of The air passage width X21 of the second main width air passage 10a and the air passage width X22 of the second sub-width air passage 10b are narrower than the air passage width X1 of the first width air passage 9. The air passage width X21 of the second main width air passage 10a and the air passage width X22 of the second sub-width air passage 10b are equal to the air passage width X31 of the third main width air passage 11a and the air passage of the third sub-width air passage 11b. Wider than width X32.

In the present embodiment, by arranging the second spacing member 42 and the third spacing member 43 offset in the air flow direction, the windward end face 43a of the third spacing member 43 is easily exposed to the air flow. . Since the airflow that hits the windward end face 43a of the third spacing member 43 is divided, the turbulence of the airflow in the first air passage 5 and the second air passage 6 can be promoted. As a result, the heat transfer coefficient and substance transfer coefficient with respect to the inner wall surfaces of the first air passage 5 and the second air passage 6 can be increased, and the total heat exchange efficiency of the heat exchange element 1 can be improved.

The ratio between the air passage width X21 of the second main width air passage 10a and the air passage width X22 of the second sub-width air passage 10b, and the air passage width X31 of the third main width air passage 11a and the third sub-width The ratio of the width of the air passage 11b to the width of the air passage X32 may be changed as appropriate. For example, when it is desired to suppress an increase in pressure loss, the air passage width X22 of the second sub-width air passage 10b is made 1.5 times as large as the air passage width X21 of the second main width air passage 10a. The air passage width X32 of the third sub-width air passage 11b may be 1.5 times the air passage width X31 of the third main width air passage 11a.

Embodiment 4.
FIG. 5 is a perspective view of the heat transfer unit 2 of the heat exchange element 1 according to Embodiment 4 of the present invention. In addition, in Embodiment 4, the same code|symbol is attached|subjected about the part which overlaps with above-described Embodiment 1, and description is abbreviate|omitted.

In the heat exchange element 1 according to the fourth embodiment, a plurality of heat transfer units 2 according to the first embodiment are arranged side by side on the same plane. Although not shown, the heat exchange element 1 is formed by alternately stacking a plurality of first heat transfer units 2a and second heat transfer units 2b arranged on the same plane. In the present embodiment, two heat transfer units 2 are provided side by side along the flow direction of the air flow and the direction orthogonal to the flow direction of the air flow. A plurality of heat transfer units 2 according to Embodiments 2 and 3 may be provided side by side along the flow direction of the air flow and the direction orthogonal to the flow direction of the air flow.

In the heat transfer unit 2, the inlets 22 of the first air passage 5 and the second air passage 6 have large opening widths. It is necessary to devise ways to maintain the strength of the surroundings. Moreover, since the air passage widths of the first air passage 5 and the second air passage 6 become narrower toward the downstream side along the air flow direction, it is necessary to suppress an increase in pressure loss. Therefore, in the present embodiment, the heat transfer unit 2 according to the first embodiment is used as one unit, and a plurality of heat transfer units 2 are provided in series along the air flow direction and the orthogonal direction. By arranging the plurality of heat transfer units 2 in the orthogonal direction, it is possible to suppress bending of the heat transfer units 2 around the inlet 22 . In addition, since a plurality of heat transfer units 2 are arranged in the air flow direction, the air flow that has passed through one heat transfer unit 2 is guided to the first width air passage 9 of the heat transfer unit 2 located on the downstream side. , the second width air passage 10 and the third width air passage 11 in that order. That is, the airflow passes through the wide and narrow air passages of one heat transfer unit 2, and then passes through the wide and narrow air passages of the next heat transfer unit 2. will pass through. In the present embodiment, since the air flow alternately passes through the wide air passage and the narrow air passage, the air passage width is narrower than when only one heat transfer unit 2 is provided in the air flow direction. It is possible to suppress an increase in pressure loss due to quenching.

Embodiment 5.
Next, the heat exchange ventilator 100 including the heat exchange element 1 will be described. FIG. 6 is a schematic diagram showing a heat exchange ventilator 100 according to Embodiment 5 of the present invention. In addition, in Embodiment 5, the same code|symbol is attached|subjected about the part which overlaps with above-mentioned Embodiment 1, and description is abbreviate|omitted.

The heat exchange ventilator 100 includes a supply air blower 14 , an exhaust air blower 15 , a heat exchange element 1 and a casing 13 . Note that FIG. 6 schematically shows the inside of the casing 13 as viewed from above.

The casing 13 is a box-shaped member that accommodates the supply air blower 14 , the exhaust air blower 15 and the heat exchange element 1 . Inside the casing 13, a supply air passage 16 through which the first air flow 7 passes and an exhaust air passage 17 through which the second air flow 8 passes are provided. The first air flow 7 is a supply air flow from the outdoor to the indoor. The second air flow 8 is the exhaust flow from the room to the outside. A supply air outlet 20 and an exhaust air inlet 19 are provided on the side surface of the casing 13 on the indoor side. A supply air intake port 18 and an exhaust air outlet 21 are provided on the side surface of the casing 13 on the outdoor side.

The supply air blower 14 is arranged in the supply air path 16 . The supply air blower 14 takes in outdoor air from the supply air inlet 18 into the supply air passage 16 to generate the first airflow 7 . The first airflow 7 flows through the supply air passage 16 and is blown into the room from the supply air outlet 20 . The supply air blower 14 sends the first air flow 7 directed from the outdoor to the indoor to the first air passage 5 shown in FIG.

The exhaust air blower 15 is arranged in the exhaust air passage 17 . The exhaust blower 15 draws indoor air from the exhaust suction port 19 into the exhaust air passage 17 to generate the second air flow 8 . The second airflow 8 flows through the exhaust air passage 17 and is blown out of the room from the exhaust outlet 21 . The exhaust air blower 15 sends the second air flow 8 directed from the room to the outside to the second air passage 6 shown in FIG.

As the heat exchange element 1, any one of the heat exchange elements 1 according to Embodiments 1 to 4 is used. The heat exchange element 1 is provided at a position where the supply air passage 16 and the exhaust air passage 17 intersect. The heat exchange element 1 performs total heat exchange between the first air flow 7 flowing through the supply air passage 16 and the second air flow 8 flowing through the exhaust air passage 17 . The heat exchange ventilator 100 recovers the sensible heat and latent heat of the exhaust flow from the room through total heat exchange in the heat exchange element 1, and transfers the recovered sensible heat and latent heat to the supply air flow. In addition, the heat exchange ventilator 100 recovers the sensible heat and latent heat of the air supply flow from the outside by total heat exchange in the heat exchange element 1, and transfers the recovered sensible heat and latent heat to the exhaust flow. . The heat exchange ventilator 100 can improve the efficiency of indoor cooling and heating and the efficiency of dehumidification and humidification, and can reduce the energy used for indoor air conditioning. The heat exchange element 1 may be configured to transfer only sensible heat between the exhaust flow and the air flow.

The configuration shown in the above embodiment shows an example of the content of the present invention, and it is possible to combine it with another known technology, and one configuration can be used without departing from the scope of the present invention. It is also possible to omit or change the part.

REFERENCE SIGNS LIST 1 heat exchange element 2 heat transfer unit 2a first heat transfer unit 2b second heat transfer unit 3 partition member 4 spacing member 5 first air passage 6 second air passage 7 first air flow , 8 second airflow, 9 first width air passage, 10 second width air passage, 10a second main width air passage, 10b second sub-width air passage, 11 third width air passage, 11a third main width air passage 11b Third sub-width air passage 12 Fourth width air passage 13 Casing 14 Supply air blower 15 Exhaust air blower 16 Air supply air passage 17 Exhaust air passage 18 Air supply inlet 19 Exhaust air inlet 20 air supply outlet, 21 exhaust outlet, 22 inlet, 31 leeward end, 41 first spacing member, 41a, 42a, 43a windward end face, 42 second spacing member, 43 third spacing member , 44 fourth spacing member, 100 heat exchange ventilator.

Claims (6)

a first heat transfer unit forming a first air passage;
a second heat transfer unit forming a second air passage,
The first air passage and the second air passage include a first width air passage extending from an air flow inlet toward the downstream side along the direction of flow of the air flow, and a downstream side of the first width air passage. and two or more second width air passages formed by branching the first width air passage into two or more,
The air passage width of the second width air passage is narrower than the air passage width of the first width air passage,
The length of the first width air passage along the flow direction of the air flow is equal to or less than the length of the approach section of the first width air passage,
The length of the second width air passage along the flow direction of the air flow is equal to or less than the length of the approach section of the second width air passage ,
The length LL of the run-up section is expressed by the formula LL = 0.056 x Re x de, where Re is the Reynolds number and de is the equivalent diameter of the first air passage or the second air passage. A heat exchange element characterized by: The first air passage and the second air passage include two or more third width air passages formed by branching the second width air passage into two or more on the downstream side of the second width air passage. further have
2. The heat exchange element according to claim 1, wherein the air passage width of the third width air passage is narrower than the air passage width of the second width air passage. 3. The heat exchange element according to claim 2, wherein the length of the third width air passage along the flow direction of the air flow is equal to or less than the length of the run-up section of the third width air passage. the first heat transfer unit and the second heat transfer unit are alternately stacked;
The first heat transfer unit and the second heat transfer unit are arranged on a partition member and form the first air passage or the second air passage between the adjacent partition members installed on the partition member. a plurality of spacing members,
The spacing member is installed between two first spacing members that define the width of the air passage of the first width, and the first spacing member to define the air passage of the second width. a second spacing member that defines a width; and a third spacing member that is installed between the first spacing members and defines the air passage width of the third width air passage,
The second spacing member is offset from the third spacing member on the upstream side along the flow direction of the air flow, and is arranged on the upstream side of the third width air passage along the flow direction of the air flow. 4. The heat exchange element according to claim 2 , wherein the heat exchange element is arranged. A plurality of said first heat transfer units and said second heat transfer units are provided side by side along the flow direction of said air flow and a direction orthogonal to said flow direction of said air flow. The heat exchange element according to any one of items 1 and 2. A heat exchange element according to any one of claims 1 to 5 ;
a supply air blower that sends a first air flow directed from the outdoor to the indoor to the first air passage;
an exhaust air blower that sends a second air flow directed from the room to the outside to the second air passage;
A heat exchange ventilator comprising: a casing that accommodates the heat exchange element, the supply air blower, and the exhaust air blower.

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